Primary transmission for high rpm motors for auxiliary drive units

ABSTRACT

A primary transmission has a first eccentric disc coupled in a fixed driving connection to a drive shaft extending into the transmission housing. An internal ring gear is mounted in the housing concentrically to the drive shaft. A first spur gear is supported on the first eccentric disc as a first drive member and meshes with the internal ring gear. The first spur gear has at least one tooth less than the internal ring gear. The diameter of the circle defined by the end of the first spur gear teeth is smaller than the diameter of the circle defined by the base of the internal ring gear teeth. The first eccentric disc has an eccentric throw that corresponds to half a difference of the circle diameters. A driven disc as a second drive member is concentric to the drive shaft and is torque-transmittingly connected to the first spur gear. One of the drive members has at least one axially projecting pin and the other has at least one receiving bore. The receiving bore has a diameter that is greater by the eccentric throw than the pin diameter. A second eccentric disc is mounted in the housing adjacent to the first eccentric disc and coupled to the drive shaft. It is identical to the first eccentric disc and provide mass compensation. The eccentric throws of the two eccentric discs are diametrically opposite one another.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The invention relates to a primary transmission for high rpm(revolutions per minute) motors for auxiliary drive units, wherein aneccentric disc is connected to the drive shaft of the motor so as torotate with the drive shaft and has supported thereon a spur gear whichacts as a first drive member. The outer toothing of the spur gearengages at a location of engagement an inner toothing of a stationarilysecured internal ring gear arranged concentrically to the drive shaft.The number of teeth of the spur gear is reduced by at least one relativeto the number of teeth of the internal ring gear. The diameter of acircle about the ends of the teeth of the spur gear is smaller by atleast one tooth height than the diameter of the circle at the base ofthe teeth of the internal ring gear. The eccentric throw of theeccentric disc relative to the center of the drive shaft corresponds tohalf the difference of the diameters of the circle about the ends of theteeth of the spur gear and of the circle about the base of the teeth ofthe internal ring gear. The spur gear is coupled in atorque-transmitting manner with a driven disc forming a second drivemember and concentrically supported relative to the drive shaft. One ofthe drive members has at least on e axially projecting pin which engagesa bore of the other drive member, and the bore has a diameter which isgreater by the amount of the eccentric throw of the eccentric disc thanthe diameter of the pin of the former drive member.

2. Description of the Related Art

Primary transmissions with a high reducing rate can be realized onmotors especially by employing worm gears. The use of a worm gear, ingeneral, also has the advantage of providing a self-locking action, butis not possible in all cases because an angular drive arrangementresults for which there is not enough space available in somesituations.

A transmission with high reducing rate is also possible by employing anopen planetary gear system in which the planet gear is embodied as aspur gear supported on an eccentric member providing the transmissionstay and meshing with a hollow gear at an engagement location. Such atransmission with high reducing rate and self-locking action is, forexample, known from U.S. Pat. No. 3,673,891. This patent relates to theuse of a rotary movement introduced into a pivot shaft having a fixedlyconnected eccentric disc for the purpose of pivoting the back rest of avehicle seat. Similar conditions are also present in a solutiondisclosed in the U.S. Pat. No. 3,667,804. In this case, there is also amanually actuated drive shaft with a fixedly connected eccentric disc onwhich a spur gear is supported whose outer toothing meshes with theinner toothing of a stationarily secured ring gear. In the disclosedembodiment the internal ring gear is a component of a mounting of a seatportion. The spur gear has at one end face thereof three projecting pinswhich engage bores at the mounting connected to the back rest whereinthese bores have an inner diameter which is larger by the amount of theeccentric throw than the outer diameter of the pin. Also, the diameterof the circle extending about the ends of the teeth of the spur gear issmaller by at least one tooth height than the diameter of the circleabout the base of the teeth of the internal ring gear. Also, the numberof teeth of the spur gear is smaller than the number of teeth of theinner toothing of the internal ring gear. The mounting which isconnectable to the back rest pivots exactly about the center point ofthe pivot shaft because the eccentric movement overlying the rotarymovement of the spur gear is compensated completely by the pins engagingthe bores in the mounting and having a smaller diameter than thesebores. In this prior art configuration which is also a self-lockingembodiment, the pivot shaft is manually driven by a hand wheel connectedfixedly to the pivot shaft, but it is conceivable to connect the pivotshaft to an electric motor. However, centrifugal forces will result forhigh rpm motor drives due to the off-center mass arrangement of theeccentric disc which will result in disruptive imbalance.

SUMMARY OF THE INVENTION

It is an object of the present invention to provide a space-saving,motor-driven primary transmission with high reducing ratio in which themass forces resulting from the imbalances can be compensated by meanswhich are identical to the components serving to transmit the torque.

In accordance with the present invention, this is achieved in thataxially adjacent to the eccentric disc supporting the spur gear at leastone further eccentric disc identical to the first eccentric disc isprovided which ensures mass compensation and which is fixedly coupled tothe drive shaft of the motor in such a way that the eccentric noses ofthe eccentric discs are positioned diametrically opposite one another.

By arranging a second eccentric disc with diametrically oppositelypositioned eccentric nose, a second centrifugal force results whichcounteracts the centrifugal force of the first eccentric disc.Accordingly, the mass forces cancel one another so that even at high rpmat the motor drive shaft quiet running condition of the drive shaft willresult. The eccentric discs are both of the same configuration. Aprimary transmission configured in this way is also self-locking.

For realizing support advantages of the drive shaft, on the one hand,and further mass compensation, on the other hand, a second spur gear issupported on the second eccentric disc. This spur gear also engages theinner toothing of the internal ring gear and acts as a transmissionmember between the drive members. On the one hand, it has at least onereceiving bore for receiving the axially projecting pins of the firstdrive member and, on the other hand, it has at least one axiallyprojecting pin for engaging a receiving bore of the second drive memberin the form of a driven disc.

Even though it is possible to provide a combination of only a single pinat the spur gear and only a single bore at the driven disc for torquetransmission, it is advantageous according to the features of theinvention to provide the first drive member in the form of the spur gearwith several axially projecting pins that are distributed uniformly on acircle which is coaxial to the bearing location of the spur gear and toprovide the same number of receiving bores in the driven disc formingthe second drive member. The receiving bores are arranged on a circle ofthe same size as that one on which the pins are arranged. However, thecircle on which the bores are arranged is coaxially positioned to thebearing projection of the driven disc supported coaxially relative tothe drive shaft in the transmission housing. This holds also true whenemploying a transmission member which is positioned between the drivemembers and is in the form of a spur gear. In this case, several axiallyprojecting pins are arranged uniformly on a circle coaxial to thebearing location of the spur gear forming the first drive member. Theaxially projecting pins engage the same number of receiving bores in thesecond spur gear forming the transmission member between the drivemembers. Several pins arranged between the receiving bores projectaxially from this transmission member and engage corresponding receivingbores of the driven disc supported coaxially to the drive shaft. For thepurpose of reducing friction or running noise, it may be advantageous tosurround the pins with anti-friction bearings, e.g. plain bearingbushings or roller bearings, which roll on the inner circumference ofthe receiving bores which are larger by the amount of the eccentricthrow than the outer diameter of the bearing bushings or rollerbearings, i.e., the pin diameter includes the respective bearing.Moreover, for reducing noise and for ease of running, it may beadvantageous to surround the pins with elastic intermediate rings whichthen receive the plain bearing bushings or roller bearings.

BRIEF DESCRIPTION OF THE DRAWING

In the drawing:

FIG. 1 shows a first embodiment of the primary transmission according tothe invention, which is flanged to an electric motor, on an enlargedscale in longitudinal section along the line I—I of FIG. 2;

FIG. 2 shows the driven disc arranged in the transmission housing insection along the line II—II of FIG. 1;

FIG. 3 shows a second embodiment of a primary transmission according tothe present invention in a longitudinal section along the line III—IIIof FIG. 4, wherein a transmission member in the form of a spur gear isarranged between the first drive member and the second drive member;

FIG. 4 shows the driven disc of the embodiment represented in FIG. 3arranged in the transmission housing in a sectional view according tothe line IV—IV of FIG. 3;

FIG. 5 shows the primary transmission according to the present inventionin an end view onto the driven side;

FIG. 6 shows on an enlarged scale relative to FIGS. 1 through 5 a pinprojecting from the first drive member or the transmission member,wherein the pin is surrounded by an elastic intermediate member on whichthe plain bearing bushing is arranged;

FIG. 7 shows another embodiment of a pin on the first drive member orthe transmission member, on a scale analog to that of FIG. 6, whereinthe pin is also surrounded by an elastic intermediate member on which,however, a roller bearing is supported;

FIG. 8 shows a third embodiment of a primary transmission according tothe present invention in which a revolving support member in the form ofa gear wheel is arranged adjacent to one of the drive members and theeccentric discs are components of an eccentric support shaft which iscoupled to the drive shaft of the motor and which penetrates a housingplate;

FIG. 9 is a fourth embodiment of a primary transmission according to thepresent invention in which on the eccentric support shaft two drivemembers are arranged adjacent to one another having receiving boreswhich are staggered relative to one another by the respective eccentricthrow and are both penetrated by a pin of the driven disc which is anintegral part of the driven disc;

FIG. 10 is a modification of the embodiment of FIG. 9 wherein the pinpenetrating the drive members is comprised of a material different fromthe material of the driven disc and is inserted into the driven disc;

FIG. 11 shows yet another embodiment of the primary transmissionaccording to the present invention in which only one spur gear acts as adrive member while the adjacently arranged spur gear is a support gearwhich rotates without contacting the penetrating pins, wherein the pinis supported in a bearing disc that is rotatably arranged in the housingplate.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

In the embodiment of the primary transmission according to the presentinvention as represented in FIGS. 1 and 2, the torque-transmittingtransmission components are encapsulated in a housing 20. Thistransmission housing 20 is cup-shaped and provided with a bottom plate21 that is seated on a collar 12 of the electrically operated motor 10and is moreover secured by screws in a non-rotating manner to the motor10. A drive shaft 11 projects from the collar 12 of the motor 10 and hasa cross-section suitable for rotating engagement. Such a cross-sectionis realized, for example, by having two flat longitudinal sides. Aneccentric disc 13 is fixedly arranged on the drive shaft 11. A firstdrive member 14 in the form of a spur wheel 15 is rotatably supported onthe eccentric disc 13 with interposition of, for example, a rollerbearing 19. The outer toothing 16 of the spur gear 15 meshes at alocation of engagement with the inner toothing 18 of an internal ringgear 17 which is a component of the cup-shaped housing 20, i.e., theinner toothing 18 is mounted on the inner circumference of thecup-shaped housing 20. Several pins 26 project in the axial directionfrom the end face of the spur gear 15 facing away from the motor 10. Inthe shown embodiment, as can be seen in FIG. 2, six such pins 26 areprovided which are uniformly distributed in the circumferentialdirection. Even though it is not absolutely required to surround orenclose the pins 26 by bushings, the pins 26 represented in FIGS. 1 and2 are provided with plain bearing bushings 37 at their circumferencewith which the pins 26 engage bores 29 of the driven disc 28 acting asthe second drive member 27. This driven disc 28 has a bearing projection30 at its central area. The projection 30 has an extension in the formof a shaft stump 32 which projects from the housing 20 coaxially to thedrive shaft 11. The bearing projection 30 of the driven disc 28 issurrounded by a roller bearing 33 which is supported in a bearing cover22 which is secured in the cup-shaped housing 20 and closes it off. Afurther eccentric disc 34 is fixedly connected on the drive shaft 11adjacent to the eccentric disc 13 in such a way that the maximumeccentric throw of the eccentric disc 34 is positioned diametricallyopposed to the maximum eccentric throw of the eccentric disc 13. Thiseccentric disc 34, which is provided for the purpose of masscompensation relative to the drive shaft 11, engages the recess 31 inthe driven disc 28 and its bearing projection 30 such that play isprovided between the inner circumference of the recess 31 and theeccentric disc 34.

As already mentioned before, the bores 29 in the driven disc 28 aredimensioned such that they are larger by the eccentric throw (eccentriclift) than the outer diameter of the bearing bushings 37 surrounding thepins 26. Moreover, it should be mentioned that the bearing cover 22 hasmultiple fastening bores 41 and 42 with which the primary transmissionand the motor 10 fixedly connected thereto can be mounted on frameparts, for example, of vehicles.

Upon rotation of the drive shaft 11 the eccentric discs 13 and 34 arealso rotated. The eccentric disc 13, in the embodiment represented inFIG. 1, also eccentrically drives the spur gear 15 so that the locationof engagement of the outer toothing 16 relative to the inner toothing 18of the stationary internal ring gear 17 will revolve circumferentially.For a difference of only one tooth between the outer toothings 16 of thespur gear 15 and the inner toothing 18 of the internal ring gear 17, onerotation of the drive shaft 11 rotates the spur gear 15 only by onetooth spacing and this rotary movement is also applied to the drivendisc 28 which thus rotates by the same rotational angle as the spur gear15. Accordingly, the greater the tooth number of the inner toothing 18,the higher the reducing ratio of the transmission.

The embodiment represented in FIGS. 3 and 4 has a transmission member 35in the form of a further spur gear 36 positioned between the spur gear15, supported on the eccentric disc 13 via the roller bearing 19 andforming the first drive member 14, and between the second drive member27 in the form of the driven disc 28 that is supported on the bearing 33within the bearing cover 22. This spur gear 36 matches with regard toits dimensions and the number of teeth the spur gear 15. The spur gear36 is supported on the eccentric disc 34 wherein a further rollerbearing 43 may be positioned between the bearing bore of the spur gear36 and the eccentric disc 34 on which it is mounted. The spur gear 36 isarranged such that, in comparison to the tooth engagement location ofthe spur gear 15, it is positioned exactly diametrically opposite at theinner toothing 18 of the internal ring gear 17 and is secured in thisposition by the eccentric disc 34.

In contrast to the spur gear 15 the spur gear 36 forming thetransmission member 35 has bores 29 which can be engaged by the pins 26surrounded by plain bearing bushings 37. The bores 29 and the plainbearing bushings 37 are dimensioned as disclosed above. Pins 26 alsoproject from the end face of the spur gear 36, functioning as atransmission member 35, at a side facing away from the motor 10. Thesepins may be surrounded by plain bearing bushings 37 or by rollerbearings 39, as shown in FIG. 3, and engage bores 38 of the driven disc28 forming the second drive member 27. It is understood that thesolution with respect to the arrangement of roller bearings 39 on thepins 26 is not limited to their arrangement in the driven disc 28.Instead, it is possible that all pins 26, also those of the spur gear15, are provided with roller bearings 39 in place of the plain bearingbushings 37.

In contrast to the solution illustrated in FIG. 1, in which the primarytransmission is a flanged transmission connected by screws 40 to themotor 10, the connection between the primary transmission and the motorcan also be in the form of an integrated transmission. For this purpose,the bottom plate 21 of the cup-shaped housing 20 is provided with a ringprojection 23 having an annular groove 24 into which an annular embossedprojection 25 provided in the mantle of the motor 10 is pressed.

The operation of the embodiment of the primary transmission illustratedin FIGS. 3 and 4 is analog to the operation of the embodiment of theprimary transmission according to the invention as illustrated in FIGS.1 and 2.

In the embodiments illustrated in FIGS. 6 and 7, the pins 26 aresurrounded by elastic intermediate rings 44 on which, as shown in FIG.6, plain bearing bushings 37 are supported or, as shown in FIG. 7,roller bearings 39 are seated. These measures are provided for noisereduction as well as tolerance compensation.

The primary transmission illustrated in FIG. 8 has a housing 20 that iscomprised of two connectable cup-shaped housing halves 53 and 54 whichcan be made for example, of synthetic material and are connected to oneanother. This connection can be of a conventional design such as a screwconnection, adhesive connection, snap connection etc. The housing half54 has a bottom part 58 with an opening 59 into which the collar 12 ofthe electric motor 10 can be inserted. The bottom part 58 can befastened to the motor by fastening screws 60 which are, for example,received in fastening bores provided in the bottom part and formed as abayonet closure. The drive shaft 11 of the motor 10 projecting into theinterior of the housing 20 is fixedly connected by a clutch 45 to theeccentric support shaft 46. The eccentric support shaft 47 is supportedin a housing plate 47 extending transversely in the housing 20 and inthe driven disc 28 which is in turn supported by the shaft stump 32projecting from the housing 20 in the bottom part of the cup-shapedhousing half 53. The driven disc 28 comprises at least one pin 26projecting into the interior of the housing 20 and engaging a receivingbore 29 of the spur gear 15 supported on the eccentric disc 34 of theeccentric support shaft 46. This receiving bore 29, as mentioned above,has a diameter that is larger by the eccentric throw than the diameterof the pin 26. However, it is understood, that, as described above, morethan one pin 26 can project from the driven disc 28 and that acorrespondingly matching number of bores 29 can be arranged in the spurgear 15. This spur gear 15 engages with its outer toothing the innertoothing 18 of the internal ring gear 17 provided at the inner housingcircumference. Upon rotation of the eccentric shaft 46, the two toothengagement locations revolve in the same manner as the eccentric disc 34so that in accordance with the difference between the toothing of thisspur gear 15 and the toothing of the internal ring gear 17 the drivendisc 28 is further rotated by the receiving bore 29 and the axiallyprojecting pin 26 engaged therein. This means that, for a difference ofone tooth between the tooth number of the spur gear 15 and the toothnumber of the internal ring gear 17, the driven disc 28 and thus alsoits shaft stump 32 is rotated by one tooth spacing when the eccentricsupport shaft 46 carries out one revolution.

On the eccentric disc 13 positioned adjacently to the eccentric disc 34a further support gear 48 is mounted which also engages the innertoothing 18 of the internal ring gear 17. The tooth engagement locationof the support gear 48 revolves in the same way as disclosed inconnection with the spur gear 15. However, the revolution of thissupport gear 48 is without effect on the driven disc 28 because thesupport gear 48 has no connection to the pins 26. It is provided with anannular groove at its end face which allows unimpaired movement of thepins 26 relative to the support gear 48. This support gear 48 provides,on the one hand, a support action for the eccentric support shaft 46and, on the other hand, mass compensation. In the primary transmissionillustrated in FIG. 8, all bearing locations are in the form of plainbearings in order to reduce cost and no bearing bushings are used.Instead, except for the metallic components, the eccentric support shaft46, and the driven disc 28, all other components are made of a syntheticmaterial (plastic) having anti-friction properties.

The embodiment of a primary transmission according to the presentinvention as illustrated in FIG. 9 has been modified in comparison tothe primary transmission represented in FIG. 8. In this modification twospur gears 15 and 36 are used which both function as drive members andtherefore are provided with bores 29 equidistantly radially spaced fromthe respective eccentric center point of the eccentric discs 13 and 34,wherein both bores 29 are penetrated by a common pin 26. It isunderstood that instead of the represented single pin 26 also severaluniformly circumferentially distributed pins can be provided on thedriven disc, and a matching number of bores 29 is then provided in eachone of the two spur gears 15, 36. The spur gears 15 and 36 are supportedin analogy to FIG. 3 via roller bearings 19, 43 on the eccentric discs13, 34. The eccentric support shaft 46 itself is supported by bearingbushings, on the one hand, in the housing plate 47 and, on the otherhand, in the driven disc 28 which itself, in analogy to FIG. 3, issupported with its shaft stump 32 by roller bearing 33 in the bottompart of the housing half 53 of the housing 20. The shaft stump 32 whichis preferably made of metal is preferably embedded in the driven disc 28made of plastic material which is possible, for example, by injectionmolding the driven disc about the respective shaft part of the shaftstump 32. In the embodiment illustrated in FIG. 9, the pin 26 shown inthis Figure can be surrounded by plastic bushings which engage thereceiving bores 29 of the spur gear 15 and 36. When using severalaxially projecting pins 26 arranged on the same circle, they can all besurrounded by bushings. The housing plate 47 adjacent to the eccentricdisc 13 has an annular groove facing the spur gears and arranged suchthat the pin ends which project past the spur gear 36 engage with playthis annular groove so that the rotational movement of the pins 26 isnot impaired. In the embodiment shown in FIG. 9, the cup-shaped housinghalf 54 flanged to the electric motor 10 is secured, to the housing half53 by radially embossed portions 57. The at least partially appliedembossed connection is also used to secure the housing plate 47 to thehousing half 53.

The primary transmission according to the invention illustrated in FIG.10 corresponds substantially to that already disclosed in connectionwith FIG. 9. However, the axially projecting pins 26 are made of ametallic material and are embedded with an end 49 having a greaterdiameter than the projecting pin end, in the same manner as the shaftstump 32, in the driven disc 28 made of plastic. In this solution, thetwo spur gears 15 and 36 are also used as torque-transmitting drivemembers. A further difference of the embodiment as represented in FIG.10 in comparison to that of FIG. 9 is that the cup-shaped housing halves53 and 54 are connected to one another by snap members 55 and countersnap members 56.

The embodiment represented in FIG. 11 of a primary transmissionaccording to the present invention corresponds in its operation to thatof FIG. 8. The throughbore 50 in the support gear 48 has nowhere contactwith the axially projecting pin 26 penetrating the receiving bore 29 andthe bore 50, wherein the axially projecting pin 26, in contrast to theprevious embodiments, is supported with the end projecting from thedriven disc 28 in bearing bores 52 of a bearing plate 51. This bearingplate 51 is supported in a matching circular recess of the housing plate47 and additionally supports the free and of the pin 26. The othercomponents illustrated in FIG. 11 corresponds substantially to thoserepresented in FIGS. 9 and 10.

While specific embodiments of the invention have been shown anddescribed in detail to illustrate the inventive principles, it will beunderstood that the invention may be embodied otherwise withoutdeparting from such principles.

What is claimed is:
 1. A primary transmission for motors operating athigh rpm for auxiliary drive units, the primary transmission comprising:a housing; a drive shaft projecting into the housing; a first eccentricdisc mounted in the housing so as to be coupled in a fixed drivingconnection with the drive shaft; an internal ring gear stationarilymounted in the housing concentrically to the drive shaft; a first spurgear supported on the first eccentric disc, the first spur gearconfigured to act as a first drive member; the first spur gear having anouter toothing cooperating with an inner toothing of the internal ringgear at a location of engagement; the first spur gear having teeth andthe internal ring gear having teeth, wherein the first spur gear has atleast one tooth less than the internal ring gear; wherein a circleextending through the end of the teeth of the first spur gear has afirst diameter and wherein a circle extending through the base of theteeth of the internal ring gear has a second diameter, wherein the firstdiameter is smaller by at least one tooth height than the seconddiameter; wherein the first eccentric disc has an eccentric liftrelative to a center of the drive shaft corresponding to half adifference between the first and the second diameters; a driven discforming a second drive member and arranged concentrically to the driveshaft, the second drive member torque-transmittingly connected to thefirst spur gear; wherein at least one of the first and second drivemembers has at least one axially projecting pin and wherein the other ofthe first and second drive members has at least one receiving bore; theat least one receiving bore having a bore diameter and the at least oneaxially projecting pin having a pin diameter, wherein the bore diameteris greater by the eccentric lift of the eccentric disc than the pindiameter; at least one second eccentric disc mounted in the housingaxially adjacent to the first eccentric disc so as to be coupled in afixed driving connection with the drive shaft, wherein the at least onesecond eccentric disc is identical to the first eccentric disc and isconfigured to compensate mass, wherein the eccentric nose of the firsteccentric disc and the eccentric nose of the second eccentric disc arepositioned diametrically opposite one another; a second spur gearsupported on the second eccentric disc and engaging the inner toothingof the internal ring gear, the second spur gear configured to act as atransmission member between the first drive member and the second drivemember, wherein the second spur gear has at least one receiving boreconfigured to receive the at least one axially projecting pin supportedon the first drive member and having at least one axially projecting pinconfigured to engage a receiving bore of the driven disc forming thesecond drive member; wherein the first spur gear has a number of theaxially projecting pins distributed at uniform angular spacing on afirst circle concentric to a bearing location of the first spur gear,and wherein the second spur gear has a number of the receiving boresmatching the number of the axially projecting pins, wherein the axiallyprojecting pins engage the receiving bores, respectively, and whereinthe second spur gear has additional ones of the axially projecting pinsarranged between the receiving bores and projecting away from the firstspur gear, wherein the second drive member is concentric to the driveshaft and has several of the receiving bores matching the number ofadditional axially projecting pins and engaging the additional axiallyprojecting pins.
 2. The primary transmission according to claim 1,wherein the second spur gear has a number of the axially projecting pinsdistributed at uniform angular spacing on a first circle concentric to abearing location of the second spur gear, wherein the driven disc has anumber of the receiving bores matching the number of axially projectingpins of the second spur gear, wherein the receiving bores are arrangedon a second circle having a size matching the size of the first circle,wherein the second circle is concentric to a collar of the driven discsupported coaxially to the drive shaft in the housing, and wherein theaxially projecting pins of the second spur gear engage the receivingbores of the driven disc, respectively.
 3. The primary transmissionaccording to claim 2, wherein the axially projecting pins of the secondspur gear have external anti-friction bearings and wherein the pindiameter is measured at an outer circumference of the anti-frictionbearings, the anti-friction bearings rolling along an innercircumference of the receiving bores of the driven disc, respectively.4. The primary transmission according to claim 3, wherein the axiallyprojecting pins have intermediate rings positioned radially inwardly ofthe anti-friction bearings.
 5. The primary transmission according toclaim 1, further comprising an eccentric support shaft on which thefirst and second eccentric discs are mounted, the eccentric supportshaft mounted in the second drive member and a housing plate of thehousing, further comprising a clutch configured to connect the driveshaft and the eccentric support shaft.
 6. The primary transmissionaccording to claim 1, wherein a tooth engagement location between thefirst spur gear and the inner toothing of the internal ring gear isdesigned differently than a tooth engagement location between the secondspur gear and the inner toothing of the internal ring gear in order toreduce noise.
 7. The primary transmission according to claim 1, whereinthe internal ring gear is an integral part of the housing, wherein thehousing has a cup-shaped part with a bottom plate configured to beconnected by screws to a collar of a motor.
 8. The primary transmissionaccording to claim 7, wherein the housing has a bearing cover configuredto cover the open end of the cup-shaped housing, wherein the drivemember comprises a shaft stump and the shaft stump is mounted in thebearing cover coaxially to the drive shaft.
 9. The primary transmissionaccording to claim 1, wherein the internal ring gear is an integral partof the housing, wherein the housing has a cup-shaped part with a bottomplate configured to be supported on a collar of a motor, wherein thebottom plate has a ring projection with an annular groove configured tobe inserted into and secured at a housing of the motor by having anannular embossed projection of the housing pressed into the annulargroove.
 10. The primary transmission according to claim 1, wherein thehousing is comprised of two cup-shaped housing halves, wherein a firstone of the housing halves is configured to be fastened to a motor andwherein a second one of the housing halves is configured to support ashaft stump of the second drive member.
 11. The primary transmissionaccording to claim 10, wherein the two housing halves have matching snapmembers and counter snap members configured to connect the two housinghalves by a snap connection.
 12. The primary transmission according toclaim 10, wherein the two housing halves have open ends configured to beinserted into one another and secured to one another by radiallyembossed portions.
 13. The primary transmission according to claim 1,wherein the fastening bores are formed as a bayonet closure.